Jaw crusher and method of operation thereof

ABSTRACT

A generally horizontal flow vertical axis jaw-type crusher is provided wherein the jaws are mounted for eccentric motion toward and away from each other and linkage means driven by at least one of the jaws is provided for synchronous compaction feeding of material to be crushed into the jaws of the crusher.

United States Patent Heinz W. Winter I:

Inventor Salt Lake City, Utah Appl. No. 747,766 Filed July 12, 1968 Patented Jan. 19, 1971 Assignee Envirotech Corporation Salt Lake City, Utah a corporation of Delaware J AW CRUST-[ER AND METHOD OF OPERATION THEREOF 9 Claims, 9 Drawing Figs.

U.S. Cl 241/30, 241/81, 241/202 Int. Cl. B02c 1/06 Field of Search. 24l/202,

[56] References Cited UNITED STATES PATENTS 1 233,192 10/1880 Bean ,241/202 2,996,261 8/1961 Picalarga..... 241/202x 3,452,938 7/1969 Michaelson 241/202 FOREIGN PATENTS 1,109,986 6/1961 Germany 241/202 1,134,873 8/1962 Germany 241/202 1,005,898 9/1965 GreatBritain 241/202 Primary Examiner-Donald G. Kelly Attorney-Stowe and Stowell ABSTRACT: A generally horizontal flow vertical axis jawtype crusher is provided wherein the jaws are mounted for eccentric motion toward and away from each other and linkage means driven by at least one of the jaws is provided for synchronous compaction feeding of material to be crushed into the jaws of the crusher.

PATENTEU JAN 1 9 l97l SHEET 1 0F 8 l hiiiiiiil jji INVENTOR HEINZ W WINTER ATTORNEYS PATENTED JAN 1 9 |97l SHEET 3 OF INVENTOR HEINZ W. WINTER /Z (/f/Z ATTORNEYS INVENTOR HEINZ W ER ATTORNEYS SHEET U UF 8 PATEN IEU JAN 1 919m w WWW PM ENTEUJAN I 9 l9?! mm 8 BF 8 INVENTOR HEINZ w WINTER ATTORNEYS .I AW CRUSIIER AND METHOD OF OPERATION THEREOF BACKGROUND OF THE INVENTION Most conventional jaw crushers are provided with at least one moveable jaw. usually supported on a horizontal shaft for eccentric motion. The jaw of the crusher oscillates or reciprocates about the horizontal axis in association with a further f xed or synchronously moveable jaw to provide a' headroom requirements of horizontal material flow-type jaw crushers permit use of such crushers in underground mining operations where headroom is a critical factor.

In addition to the low headroom requirements of horizontal material flow jaw-type crushers, the low profile of such apparatus pennits mobile operation of such machines as heavy foundations or supporting bases are substantially eliminated.

THE PRESENT INVENTION The present invention is particularly directed to an improved horizontal material flow, vertical axis, oscillatory, jawtype crusher having means to insure a more uniform flow of material through the jaws of the cmsherand to means for synchronizing the jaws and the compaction feeding means which materially reduces the cost of manufacture by eliminating separate drive means for the feeder.

The present invention also provides means whereby the horizontal flow of material insures high throughput with a minimum of choking or clogging andlto such feed means which assist in maintaining an effective flow profile of material through the cnisher jaws.

These and other objects and advantages are provided in a horizontal flow vertical axis jaw-type crusher wherein at least one of the jaws thereof is mounted for eccentric motion toward and away from the other of said jaws, and means for synchronously feeding material into and between the jaws, wherein said feeding means comprises linkage means connected to the eccentrically mounted jaw for reciprocating the feeder in a direction opposite to the reciprocating component of the eccentrically mounted jaw; the invention is also provided in a method of operating a horizontal flow generally vertical axis jaw crusher and feed mechanism therefor which generally comprises the steps: moving at least one of the jaws in an eccentric path generally toward and away from the other of the jaws; converting the eccentric motion of the said one crusher jaw into opposed reciprocating motion and utilizing the converted opposed reciprocating motion to positively forwardly compact material to be crushed into the crusher jaws.

The invention will be more fully described in reference to the accompanying drawings wherein:

FIG. I is an elevational view of an improved jaw jaw-type amber constructed in accordance with the teachings of the present invention;

FIG. 2 is an enlarged partial fragmentary view of the operating portion of the crusher illustrated in FIG. I; I

FIG. 3 is a vertical sectional view substantially on line 3-3 of FIG. 1;

FIG. 4 is a top plan view of the reciprocating compaction grizzly employed in the apparatus illustrated in FIG. I;

FIG. 5 is a vertical sectional view substantially on line 5-5 of FIG. 4;

FIG. 6 is an enlarged fragmentary sectional view on line 6-6 of HG. I;

FIG. 7 is a fragmentary partial sectional view on line 7-7 of FIG. 8;

FIG. 8 is an enlarged substantially horizontal sectional view through the operating mechanism of the jaw crusher of FIG. I; and

FIG. 9 is a diagrammatic horizontal view of the means for converting the eccentric or oscillatory motion of the jaws of the crusher into synchronous opposed reciprocating motion.

Referring to the drawing and. in particular. to FIGS. I and 3, I0 generally designates a mobile jaw-type crusher constructed in accordance with the present invention which generally includes a main frame 12, crusher assembly 14, material storage section 16 and material compaction feeding means I8.

The main frame assembly I2 includes a pair of spaced I- beams 20 and 22, which are maintained in their spaced relation by suitable crossbeams such as crossbeams 24 shown in FIG. 3. The forward end of the main frame I2 is supported on steerable wheel assembly means 26 having a yoke or fork, not shown, for attachment to a towing vehicle. The rearward end 28 of the main frame is supported on wheels 30 rotatably mounted on a fixed axle 32.

As more clearly shown in FIG. I, the main l-beams 20 and 22 have a slight slope from the rearward end 28 toward the forward end, however, the bed of the vehicle may be horizontal or may have a greater or lesser slope than that illustrated in the drawing. The frame structure also includes a plurality of generally vertically extending rib members 34 suitably braced by further webbing 36 to support a large open hopper 38 for storage of the material to be crushed.

' The hopper 38 has generally converging sidewalls 40 which feed to a reduced area opening 42, having a generally vertically extending outlet skirt 44, which directs material to be crushed into the compaction feeder means I. As more clearly shown in FIG. 2, the outlet skirt 44 has its side edges 48' sloping downwardly from the rear walls 50 to the frontwall 52 at substantially the same angle of slope as the main frame I'- beams 20 and 22, for purposes which will be more readily apparent hereinafter.

TI'IE CRUSHER MECHANISM Referring particularly to FIGS. I, 2, 6, 7 and 8, the crusher mechanism per se is housed in a boxlike frame 56, consisting of a top plate 60, a bottom plate 62. a forward end plate 64 and rear plates 66 and 68 suitably welded and bolted together to form a rigid support or housing for the crusher. The bottom plate 62 is mounted on the main frame members 20 and 22. Adjacent the rearward end of the bottom plate 62 and ad jacent the lateral edges thereof are mounted a pair of bearing members 70 and 72 which journal the lower ends are eccentric drive shaft means 74 and 76 respectively. The upper ends of eccentric shafts 74 and 76 are joumaled in corresponding bearing means 78 and 80 mounted on the upper surface of the top plate 60.

The shafts 74 and 76. as more clearly shown in FIG. 7. in clude concentric shaft portions 82 and 84, which are received in the bearing means 70 and 78 and 72 and .0 respectively, and eccentric portions 86 and 88 which are journaled in bores in the pair of jaw members 90 and 92. Between each of the pair of eccentric bearing portions 86 and 88 is an offset counter balance portion 94 which reducesvibration during rotation of the pair of shafts 74 and 76.

The upper end of each shaft projects into drive gear housing means IQO and 102 for shafts 74 and 76 respectively. A pair of motors I04 and I06, having output shafts I and "6. drive their respective shafts 74 and 76 through suitable gear means, notshown in the drawing, and the gear means include a cm shah I12 which synchronizes the rotation of shafts 74 and 76. While in the illustrated form of the invention dual motors 104' and 106 are shown as driving the pair of shafts 74 and 76, it will be recognized that only a single motor may be employed and that drive for the other of the shafts could be solely through, for example, the cross-shaft 112 or the pair of shafts 74 and 76 could be interconnected by chain means to a single drive motor.

The pair of crusherjaws 90 and 92, each has a forwardly extending cantilevered wing portion 116 and 118 respectively, the inner faces of which are fitted with removable crusher wear plates 120 and 122 secured to the wing portions 116 and 118 by welding, or, for example, bolts 124, whereby the wear plates may be reversed after wear or inverted and replaced. The forward end of the cantilevered portions of the jaws 90 and 92 are suitably received in toggle linkage means 130 and 132. The toggle linkage means 130 and 132 are identical in form, and are described in detail in my application entitled Toggle Link Means", filed on even at date herewith, Ser. No. 747,768, filed July 12,1968, now US. Pat. No. 3,479,904.

Since the toggle link means 130 are identical in form and are described in said copending application in detail only toggle link means 130 will be briefly described herein. Toggle link means 130 includes a link member 134 having hemicylindirical bearing means 136 and 138 at opposite ends thereof. Bearing means 136 engages a nylon bearing shaft 140 joumaled in the extended end of jaw element 116. The hemicylindrical bearing 130 engages a similar nylon bearing shaft 142 carried by an overload release support block 144 normally slidably mounted on the forward end wall 64 of the crusher housing 58. The releasable slide block 144 is secured to a vertical web 148 by a long bolt 150 which is adapted to part under overload conditions to thereby permit the block 144 to slide laterally outwardly, thereby releasing the forward end of its cooperating jaw 90.

Also at the forward end of each of the jaws 90 and 92 are spring-type tie means generally designated 152 and 154 respectively. The tie means 152 and 154 each includes a tie rod 156, having a furcated end 158 pin connected to a wing element 160 of its respective crusher jaw. The extended outer end of each of the tie rods 1S6 passes through an enlarged bore in vertical plate means 162 forjaw 90 and 164 for jaw 92. The extended ends are spring-biased by helical spring means 166 and locknuts 168 to thereby urge the extended and cantilevered ends 116 and 118 of the jaws of the crusher in an outwardly direction while still permitting relative inward motion upon actuation of the drive means 104 and 106.

FEED MECHANISM Referring particularly to FIGS. 2, 3, 4, and 5, the feeding and selective sizing of the material for the crusher jaws is performed by means generally designated 18 as hereinbefore generally described. The means 18 includes reciprocating frame member 200 having a relatively flat forward portion 202 and a hopper-type rearward portion 204. The hoppertype rearward portion 204 includes sidewalls 206 and 208 and rear wall 210. The bottom of the rear portion 204 includes a plurality of spaced beams 212, 214, 216 and 218 which slope downwardly from the rear wall 210.

Referring specifically to FIG. 2, it will be seen that material is initially deposited primarily upon the upper sloping faces of the bars 212 through 218. In the illustrated form of the inventionthe bars 212 through 218 are at about a 20 angle to the lower frame member 220 of the reciprocating portion of the feeder. This angle, alpha, may be increased or decreased depending upon the amount of compaction-feeding that is desired and to some extent upon the type of material to be fed into the crusher jaws. It will be particularly noted from FIGS. 2 and that the sloping bars 212 through 218 terminate just short of the forward edge 52 of the feed spout 44 of the storage hopper 38 and the edges 224 of these members 212 through 218 provide additional pushing force for material to be fed into the jaws as to be more fully described hereinafter.

In addition to the bars 212 through 218 providing the initial compacting and feeding action for material to be fed to the jaws of the crusher segregation of the material is provided by the spaces between the bars. These bars are so mounted that fine material and material having a predetermined size falls through the spaces between the bars on to a conveyor mechanism generally designated 226 positioned below the hopper and the crusher to remove crushed material to a rearward discharge position.

The endless belt conveyor 226 includes a forward idler pulley 228 and an endless belt 230 having an upper active flight 232 and a lower return flight 234. The upper active flight is supported by a plurality of conventional idler rollers 236, 2360 and 236b to provide a troughlike catcher and supporter for crushed material, as more clearly shown in FIGS. 3 and 7 of the drawing.

The forward end 202 or grizzly portion of the reciprocating feeder 200 is generally formed of a pair side rail members 250 and 252 with a generally rectilinear center platform 254 mounted therebetween on cross bars 256 and 258. The relationship between the crusher jaws and the center platform 254 is more clearly illustrated in FIG. 8 with the platform having tapered forward edges 260 which generally conform to the conveyance of the inner opposed faces of the jaws and $2. This platform 254 supports material maintained between the crusher faces 262 and 264. The space between the lateral edges of the platform 254 and the side rails 250 and 252 permit material crushed, to a predetermined size, to fall from between the jaws of the crusher on to the active surface 232 of the conveyor belt assembly 226.

It will be particularly noted that the bottom plate 62 of the crusher frame 58 is provided with a rectangular opening 63 over which reciprocates the forward end of the feeder mechanism.

Extending between the rearward end 266 of the platform 254 and the forward edges 224 of the sloping grizzly bars 212 through 218 is a further platform 268, which is provided at its most rearward end with a horizontal plate 270 which directs material, smaller than the size of the spaces 262 and 264 and the spaces between the grizzly bars 212 through 218, on to the active surface 232 of the conveyor 226.

The entire feeder mechanism 200 is mounted for reciprocation, below the storage hopper 38 and below the crusher jaws, on a fixed frame consisting primarily of a pair of longitudinally extending beams 300 and 302 which are welded or otherwise secured to the upper surface of the bottom plate 62 of the housing 58 at their forward ends and upon suitable cross beams or sleepers 304 rearwardly thereof as shown, for example, in FIGS. 2 and 3 of the drawing. The spacing between the opposed faces of these beams 300 and 302 is such that beams 250 and 252 will freely slip therein as shown in FIGS. 3 and 7. Beams 250 and 252 are mounted therein by a plurality of rocker links 306. Each of the rocker links 306 has its upper end journaled in stub shafts 308 projecting laterally, at spaced intervals, from each of the side members 350 and 252 of the reciprocating feeder frames and from corresponding stub shafts 310 projecting laterally from the pair of spaced beams 300 and 302 as more clearly illustrated in FIGS. 2 and 3 of the drawing. By mounting the reciprocating feeder frame 200 vie the plurality of rocker links 306, it will be seen that the feeder frame, including its hopper structure formed by walls 206, 208 and 210, is free to move longitudinally of the main frame 12 which rigidly carries the crusher assembly 58.

DRIVE FOR FEEDER FRAME As hereinbefore set forth, the feeder mechanism 200 is reciprocated in synchronism with the oscillation of the eccentrically mounted jaws 90 and 92 of the crusher. Referring particularly to FIGS. 1, 6, 8 and 9, wherein the drive mechanism for the feeder frame 200 is more clearly illustrated, each of the barrel portions 320 and 322 of the crusher jaw members 90 and 92, respectively, is provided with a rearwardly extending plate or ear member 324 and 326, respectively. Each of the plates 324 and 326 is pivotally connected to link 328 and 330 respectively via pivot pins 332 and 334. The rearward ends of each of the links 328 and 330 is then connected to a rocker link 336 and 338, respectively, via pivot pins 34!) and 342. The rocker links 336 and 338 are mounted for, pivotal movement from the vertical rear wall members 66 and 68 of the boxlike support for the crusher jawsvia pivot pins 344 and rods 356 and 358 pass. Springs and suitable locknuts and washers generally designated 368, complete the assembly.

OPERATION.

From the foregoing description and in reference particularly to FIGS. 8 and 9, it will be seen that is the motors 104 and 106 rotate shafts 74 and 76, the eccentrically mounted jaw members 90 and 92 follow an orbital path such that the jaws move inwardly and forwardly thence outwardly and rearwardly during each rotation of each of the shafts 74 and 76. This orbital or eccentric movement of each of the jaws 90 and 92 is converted to essentially straight line opposite-indirection reciprocatory motion via the ears 324 and 326, secured to the rearward end of each of the barrel portions of the jaws 90 and 92, links 328 and 330, rocker links 336 and 338 and connecting rods 356 and 358. The primary conversion of the direction of motion is brought about by the rocker links such thatas the jaws move outwardly and rearwardly, the rearward motion is converted to straight line forward reciprocating motion. This action is diagrammed in FIG. 9.

In an illustrated embodiment of the invention, with the jaws I 90 and 92 having a height of 14 inches and a length of 33 inches, the shafts 74 and 76 are eccentrically mounted to the jaws to provide a maximum inward motion, for each'of the rearward ends of each of the jaws of about one-half inches and a corresponding inward movement at each of the forward ends of the jaws. Due to the offcenter mounting of the rocker links 336 and 338, the slight eccentric motion of the crusher jaws is converted to straight line reciprocating motion of approximately about 1 inch. This reciprocating movement of the feeding mechanism 200 provides for positive compaction of the material to be crushed in the crusher jaws with the compaction primarily taking place as the jaws are moving rearwardly and outwardly. This synchronized control of the feeder, from the jaws of the crusher, insures a maximum throughput of the material to be crushed and in the example given above crushing rates from about 50 tons to 100 tons an hour, are readily illustrated example is not by way of limitation but merely illustrates one form of apparatus embodying the principles of the present invention. For example, it will be recognized that the conversion of the eccentric motion of the crusher jaws into straight line reciprocating motion such that about one-half inch movement of the crusher jaws provides for about 1 inch movement of the feeder mechanism may be variously modified by merely changing the points of pivotal connection of the rocker links 336 and 338 to the main frame of the vehicle.

lclaim: 1 c

l. A method of operating a horizontal material flow generally vertical axis jaw crusher and feed mechanism therefor comprising the steps of moving at least one of the jaws in an eccentric ath generally toward and away from the a classifier and feeder mounted for reciprocation below the jaws and means for synchronously reciprocating the classifier and feeder in response to eccentric motion of the said at least one jaw comprising linkage means connected to the eccentrically mounted jaw for reciprocating the feeder and classifier in a direction opposite to the reciprocating component of the eccentric motion of the jaw.

3. in a generally horizontal flow, vertical axis jaw-type crusher wherein at least one of the jaws thereof is mounted for eccentric motion toward and away from the other of said jaws, a classifier and feeder mounted for reciprocation below the jaws, and means for synchronously reciprocating the classifier and feeder in response to eccentric motion of the said at least one jaw comprising, a rocker arm, means connecting one end of the eccentrically mounted jaw to one end of the rocker arm,

and means connecting the other end of the rocker arm to said feeder and classifier.

4. The invention defined in claim 2 wherein the classifier and feeder reciprocates at least in part below a storage hopper for material to be crushed.

5. The invention defined in claim 4 wherein the classifier and feeder includes a sloping end wall at the end remote from the jaws of the crusher to compact the material, in the normal direction of flow of material, into the crusher jaws.

6. The invention defined in claim 4'wherein the classifier and feeder includes a generally vertical offset zone in the bottom wall thereof upstream of the crusher jaws. v

7. The invention defined in claim 2 wherein each of the crusher jaws is eccentrically mounted, the crusher jaws synchronously driven and each of the eccentrically mounted jaws assists in reciprocating the classifier and feeder.

8. The invention defined in claim 5 wherein the classifier and feeder includes a generally vertical offset zone in the bottom walls thereof upstream of the crusher jaws.

9. The invention defined in claim 3 wherein each of the crusher jaws is eccentrically mounted, thecrusher jaws are synchronously driven and each of the eccentrically mounted jaws assist in reciprocating the classifier and feeder. 

2. In a generally horizontal flow vertical axis jaw-type crusher wherein at least one of the jaws thereof is mounted for eccentric motion toward and away from the other of said jaws, a classifier and feeder mounted for reciprocation below the jaws and means for synchronously reciprocating the classifier and feeder in response to eccentric motion of the said at least one jaw comprising linkage means connected to the eccentrically mounted jaw for reciprocating the feeder and classifier in a direction opposite to the reciprocating component of the eccentric motion of the jaw.
 3. In a generally horizontal flow, vertical axis jaw-type crusher wherein at least one of the jaws thereof is mounted for eccentric motion toward and away from the other of said jaws, a classifier and feeder mounted for reciprocation below the jaws, and means for synchronously reciprocating the classifier and feeder in response to eccentric motion of the said at least one jaw comprising, a rocker arm, means connecting one end of the eccentrically mounted jaw to one end of the rocker arm, and means connecting the other end of the rocker arm to said feeder and classifier.
 4. The invention defined in claim 2 wherein the classifier and feeder reciprocates at least in part below a storage hopper for material to be crushed.
 5. The invention defined in claim 4 wherein the classifier and feeder includes a sloping end wall at the end remote from the jaws of the crusher to compact the material, in the normal direction of flow of material, into the crusher jaws.
 6. The invention defined in claim 4 wherein the classifier and feeder includes a generally vertical offset zone in the bottom wall thereof upstream of the crusher jaws.
 7. The invention defined in claim 2 wherein each of the crusher jaws is eccentrically mounted, the crusher jaws synchronously driven and each of the eccentrically mounted jaws assists in reciprocating the classifier and feeder.
 8. The invention defined in claim 5 wherein the classifier and feeder includes a generally vertical offset zone in the bottom walls thereof upstream of the crusher jaws.
 9. The invention defined in claim 3 wherein each of the crusher jaws is eccentrically mounted, the crusher jaws are synchronously driven and each of the eccentrically mounted jaws assist in reciprocating the classifier and feeder. 